EP1362194B1 - Electro mechanical brake tightening device - Google Patents

Electro mechanical brake tightening device Download PDF

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Publication number
EP1362194B1
EP1362194B1 EP02710051A EP02710051A EP1362194B1 EP 1362194 B1 EP1362194 B1 EP 1362194B1 EP 02710051 A EP02710051 A EP 02710051A EP 02710051 A EP02710051 A EP 02710051A EP 1362194 B1 EP1362194 B1 EP 1362194B1
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EP
European Patent Office
Prior art keywords
brake
application device
measuring
brake application
electromechanical brake
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP02710051A
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German (de)
French (fr)
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EP1362194A1 (en
Inventor
Josef Staltmeir
Thomas Wagner
Ulf Friesen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
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Publication of EP1362194A1 publication Critical patent/EP1362194A1/en
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Publication of EP1362194B1 publication Critical patent/EP1362194B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/2245—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members in which the common actuating member acts on two levers carrying the braking members, e.g. tong-type brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F16D2066/005—Force, torque, stress or strain

Definitions

  • the invention is based on an electromechanical brake application device, especially for a rail vehicle brake, according to the genus of Claim 1.
  • electro-pneumatic brake systems there are currently three braking systems in the rail vehicle sector used: electro-pneumatic brake systems, electro-hydraulic Brake systems and electromechanical brake systems.
  • the braking system can be designed as an active or passive braking system, depending on whether the Force of a brake actuator for braking (active braking system) or for releasing the brake (passive braking system) must be applied.
  • active braking system active braking system
  • passive braking system passive braking system
  • DE 199 45 701 A1 describes an electromechanical brake application device known for rail vehicles with a brake actuator, the service brake unit and a storage brake unit with an energy store includes.
  • the service brake unit includes a brake force generator for application and / or releasing the brake, for example in the form of an electromotive Drive.
  • the storage brake unit comprises at least one energy store for storing and releasing energy for applying the brake as an operational emergency brake in the sense of an underlying safety level in the event of failure the service brake unit and / or as a parking or parking brake.
  • the memory brake unit is generally designed as a spring brake.
  • a power converter ensures the implementation of the braking force generator and / or energy released by the energy store into a brake application movement.
  • the electric motor drive is through a control and power electronics controllable for slip-controlled or load-corrected braking.
  • values for the actual braking force present are necessary, so that sensors for immediate braking force measurement or for measurement of sizes must be provided from which the actual braking force can be derived is.
  • electropneumatic and electrohydraulic brake systems generally pressure sensors for measuring the in the compressed air or in the Hydraulic fluid existing operating pressure used, from which the Amount of the instantaneous braking force can be derived.
  • electromechanical systems however, such media are not available.
  • the generic US-A-4 805 740 describes an electromechanical Brake application device with a brake actuator for applying and / or releasing the brake and with a power converter for the implementation of the brake actuator emitted energy in a brake application movement, the Power converter arranged in the power flow, with at least one sensor for indirect or direct braking force measurement Includes shear force measuring pin.
  • the sensor is replaced by two strain gauges formed, which are connected in a half bridge, which with a removed from the shear force measuring bolt arranged additional half bridge, one variable resistance and an amplifier through appropriate lines stay in contact. Because of the assignment of the individual lines to Connect the half-bridge consisting of the strain gauges at the measuring location specialists to the rest of the measuring device. It also complicates decentralized arrangement of the components a simple assembly or a quick exchange of the measuring device in total.
  • the present invention is based on the object, a Electromechanical brake application device of the type mentioned at the beginning create, in which the assembly, exchange or retrofitting of Measuring device is simplified.
  • the evaluation electronics in the bolt head of the shear force measuring bolt is included, the shear force measuring bolt forms a complete measuring module, which provides the braking force control with signals that are proportional to the actual braking force are.
  • the resistance signal provided by the strain gauges ⁇ R by the evaluation electronics into an analog signal (-10 V up to + 10V) or a digital signal proportional to the braking force.
  • the shear force measuring pin according to the invention as a self-contained Measuring module integrated in the control circuit of any brake application devices which greatly simplifies assembly, replacement or retrofitting.
  • the shear force measuring pin then only has a standardized one Interface on, which also from non-torch forces to a braking force control device can be connected.
  • the mechatronic shear force measuring pin combines with force conversion and simultaneous force measurement two functions in themselves. Therefore, the invention Build brake application device on the one hand, on the other hand there are fewer components and a lower weight. By the force sensor is integrated directly and immediately into the power flow of the power converter, results there is also high measuring accuracy.
  • the shear force measuring pin can be designed mechanically highly durable to ensure a safe Power transmission.
  • the shear force measuring pin forms a hinge pin of at least two force transmission elements of the power converter connecting joint.
  • the joint directs a connecting rod that can be actuated linearly by the brake actuator to one Brake lever of an eccentric arrangement acting on brake shoes.
  • the force measuring point is in the immediate vicinity of the force acting point, which is why the influence of Disturbances such as bearing friction or hysteresis is small, so that very precise measurements are possible.
  • a preferred measure provides that the sensor for braking force measurement at least one strain gauge held on the circumference of the shear force measuring bolt includes.
  • Strain gauges are known to have high measuring accuracy with a wide measuring range at the same time and are insensitive to Temperature changes and pressure surges, which is especially true in the context of Emergency braking sudden force is advantageous. About that they are characterized by good long-term stability and high corrosion resistance out.
  • redundant sensors and / or redundant ones Sensor signal evaluation electronics, in particular redundant sensors with different measuring principles and / or redundant sensor signal evaluation electronics different construction and type. So that will an increased reliability of the measuring arrangement is achieved, moreover a plausibility check is carried out possible by comparing the measurement signals of two or more measuring circuits.
  • the preferred embodiment of an electromechanical, designated overall by 1 in FIG Brake application device is provided for a rail vehicle and includes a brake actuator 2 with a service brake unit and one Brake unit.
  • the service brake unit has an electric drive, for example an electric servomotor 4, which is in an actuator housing 6 of the Brake actuator 2 is housed.
  • a mechanical force converter 8 is used for Conversion of the energy output by the brake actuator 2 into a brake application movement.
  • the actuator 4 sets a coaxial brake spindle 10 in rotation, which by the power converter 8 in a brake application movement of brake pads 12 in Direction to be converted to a brake disc 14.
  • the power converter 8 includes including a spindle / nut assembly 16 with one on the brake spindle 10 rotatably mounted spindle nut 18, which 10 linear movements when the brake spindle rotates can run in the direction of the spindle axis. That from the servomotor 4 opposite end of the brake spindle 10 projects into a cylindrical hollow section a connecting rod 20, which is axially fixed to the spindle nut 18.
  • Storage spring 24 is biased in the brake release position.
  • the storage spring 24 is part of the storage brake unit and serves as an energy storage for storage and Delivering energy to apply the brake as an operational emergency brake in the In the sense of an underlying security level in the event of failure of the service brake unit and / or as a parking or parking brake. Both the service and storage brake unit act on the connecting rod 20.
  • the spring 24 is by a locking device 26 held in the biased position.
  • a plate-shaped connecting rod head 28 of the connecting rod 20 protrudes from the sliding sleeve 22 and is provided with a connecting rod eye 30.
  • a pivot pin 32 projects through the connecting rod eye 30 and coaxially with it Through bores 34 of the connecting rod eye 30 axially encompassing at one end a cheek 38 formed cheeks 38.
  • the cheeks 38 of the brake lever 36, the connecting rod head 28 and the joint pin 32 together form a joint 40 of the power converter 8, whereby the brake lever 36 on the connecting rod 20 perpendicular to Spindle axis 42 is articulated.
  • the storage spring 24 becomes due to the connecting rod 20, which then extends axially, the joint pin 32 among other things by shear forces acting essentially perpendicular to the pin axis 44 claimed.
  • the other end of the brake lever 36 acts on an eccentric arrangement with a Eccentric shaft 46, which is articulated to a pliers lever 48, which together with another caliper lever 50 forms a brake caliper 52.
  • a pliers lever 48 which together with another caliper lever 50 forms a brake caliper 52.
  • the caliper levers 48, 50 are each pad holders 54 with brake pads 12, which are displaceable in the direction of the axis of the brake disc 14.
  • the one from the Brake pads 12 opposite ends of the caliper levers 48, 50 are together connected via a push rod actuator 56, which is preferably electrically is actuated.
  • the arrangement described also forms part of the Power converter 8, which caused by the servomotor 4 or the storage spring 24 Extension movements of the connecting rod 20 in a brake application movement of the Brake pads 12 converts towards the brake disc 14.
  • the shear force measuring bolt is with at least one Provide sensor 60 for measuring quantities from which the to Brake pads 12 acting braking force can be derived indirectly or directly.
  • the sensor is made using strain gauges (DMS) 60 formed, for example, in a plane perpendicular to the bolt axis 44 circumferential grooves 62 are added.
  • the grooves 62 with the strain gauges 60 are located in the area of the axial joints of the connecting rod head 28 with the cheeks 38 of the brake lever 36 and thus exactly in the shear plane of the shear force measuring pin 58 subjected to shear.
  • the strain gauges 60 are preferably on the circumference of the shear force measuring bolt 58 by gluing attached that they are caused by the opposing shear forces Shear deformations of the shear force measuring pin 58 generate proportional signals and deliver them to evaluation electronics 64.
  • strain gauges 60 can also be applied directly the outer surface of the shear force measuring pin 58 can be fixed.
  • one or more strain gauges 60 can also be Brake lever 36 may be arranged to the from the deformation of the brake lever 36 To be able to derive braking forces.
  • any other type of sensor can be used with which the deformations of the shear force measuring bolt 58 occurring during operation and / or the brake lever 36 can be measured, for example in the shear force measuring bolt 58 integrated pressure transmitters, which are preferably based on capacitive, work piezoelectric or piezoresistive principle.
  • the measuring sensors 60 and / or the evaluation electronics 64 can be provided redundantly. In particular can also redundant sensors with different measuring principles and redundant Evaluation electronics of various designs and types are available.
  • the shear force measuring pin 58 has an end-side, enlarged in diameter Bolt head 66, in which a sensor signal evaluation electronics 64 are accommodated is, preferably in that it is cast into the bolt head 66, whereby a vibration-damping or vibration-decoupled recording is given.
  • a strain gauge 60 contains the evaluation electronics 64 a strain gauge bridge circuit.
  • the end of the shear force measuring pin 58 pointing away from the pin head 66 has two outer grooves 68 extending transversely to the pin axis 44 for receiving one position-securing snap ring.
  • a conversion of the shear deformation signals also takes place in the evaluation electronics 64 in signals for the actual braking force acting on the brake pads 12 instead, which to a control and regulation device, not shown forwarded to a desired based on a target-actual comparison To be able to adjust the target braking force.
  • the received signals also serve for the actual braking forces for monitoring the force control and functionality the brake application device 1 for safety-relevant braking.
  • Verification of the measurement results can also be done by a Current sensor measured motor current compared with the signal for the actual braking force become.

Abstract

An electromechanical brake tightening device for a rail vehicle, includes a brake actuator to apply and release brakes. The actuator has a power converter to convert energy supplied by the brake actuator to a brake application movement. The power converter includes a shear force measuring bolt and/or a brake lever, arranged in a power transmission path of the converter to measure braking power.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer elektromechanischen Bremszuspanneinrichtung, insbesondere für eine Schienenfahrzeugbremse, nach der Gattung des Patentanspruchs 1.The invention is based on an electromechanical brake application device, especially for a rail vehicle brake, according to the genus of Claim 1.

Im wesentlichen werden derzeit im Schienenfahrzeugbereich drei Bremssysteme eingesetzt : Elektropneumatische Bremssysteme, elektrohydraulische Bremssysteme sowie elektromechanische Bremssysteme. Das Bremssystem kann dabei als aktives oder passives Bremssystem ausgeführt sein, je nachdem ob die Kraft eines Bremsaktuators zum Einbremsen (aktives Bremssystem) oder zum Lösen der Bremse (passives Bremssystem) aufgebracht werden muß. Für den Fall von Betriebsstörungen erfolgt bei elektropneumatischen Systemen eine Energiespeicherung in Druckluftbehältern, bei elektrohydraulischen Systemen in Hydrobehältern und bei elektromechanischen Systemen in Form von Speicherfedern.There are currently three braking systems in the rail vehicle sector used: electro-pneumatic brake systems, electro-hydraulic Brake systems and electromechanical brake systems. The braking system can be designed as an active or passive braking system, depending on whether the Force of a brake actuator for braking (active braking system) or for releasing the brake (passive braking system) must be applied. In the case Energy malfunctions occur in electropneumatic systems in compressed air tanks, in electrohydraulic systems in hydraulic tanks and with electromechanical systems in the form of storage springs.

Aus der DE 199 45 701 A1 ist eine elektromechanische Bremszuspanneinrichtung für Schienenfahrzeuge mit einem Bremsaktuator bekannt, der eine Betriebsbremseinheit sowie eine Speicherbremseinheit mit einem Energiespeicher umfaßt. Die Betriebsbremseinheit beinhaltet einen Bremskrafterzeuger zum Zuspannen und/oder Lösen der Bremse, beispielsweise in Form eines elektromotorischen Antriebs. Die Speicherbremseinheit umfaßt mindestens einen Energiespeicher zum Speichern und Abgeben von Energie zum Zuspannen der Bremse als betriebliche Notbremse im Sinne einer unterlegten Sicherheitsebene bei Ausfall der Betriebsbremseinheit und/oder als Park- oder Feststellbremse. Die Speicherbremseinheit ist im allgemeinen als Federspeicherbremse ausgebildet.DE 199 45 701 A1 describes an electromechanical brake application device known for rail vehicles with a brake actuator, the service brake unit and a storage brake unit with an energy store includes. The service brake unit includes a brake force generator for application and / or releasing the brake, for example in the form of an electromotive Drive. The storage brake unit comprises at least one energy store for storing and releasing energy for applying the brake as an operational emergency brake in the sense of an underlying safety level in the event of failure the service brake unit and / or as a parking or parking brake. The memory brake unit is generally designed as a spring brake.

Ein Kraftumsetzer sorgt für eine Umsetzung der vom Bremskrafterzeuger und/oder vom Energiespeicher abgegebenen Energie in eine Bremszuspannbewegung. Der elektromotorische Antrieb ist durch eine Regelungs- und Leistungselektronik zu schlupfgeregelten oder lastkorrigierten Bremsungen ansteuerbar. Für den Soll-Ist-Vergleich sind Werte für jeweils vorliegende Ist-Bremskraft notwendig, so daß Sensoren zur unmittelbaren Bremskraftmessung oder zur Messung von Größen vorgesehen werden müssen, aus denen die Ist-Bremskraft ableitbar ist.A power converter ensures the implementation of the braking force generator and / or energy released by the energy store into a brake application movement. The electric motor drive is through a control and power electronics controllable for slip-controlled or load-corrected braking. For the target-actual comparison, values for the actual braking force present are necessary, so that sensors for immediate braking force measurement or for measurement of sizes must be provided from which the actual braking force can be derived is.

Bei elektropneumatischen und elektrohydraulischen Bremssystemen werden im allgemeinen Drucksensoren zur Messung des in der Druckluft oder in der Hydraulikflüssigkeit vorhandenen Betriebsdrucks verwendet, aus dem dann die Höhe der momentanen Bremskraft ableitbar ist. Bei elektromechanischen Systemen sind solche Medien jedoch nicht vorhanden.With electropneumatic and electrohydraulic brake systems generally pressure sensors for measuring the in the compressed air or in the Hydraulic fluid existing operating pressure used, from which the Amount of the instantaneous braking force can be derived. With electromechanical systems however, such media are not available.

Die gattungsbildende US-A-4 805 740 beschreibt eine elektromechanische Bremszuspanneinrichtung mit einem Bremsaktuator zum Zuspannen und/oder Lösen der Bremse und mit einem Kraftumsetzer zur Umsetzung der vom Bremsaktuator abgegebenen Energie in eine Bremszuspannbewegung, wobei der Kraftumsetzer einen im Kraftfluß angeordneten, mit wenigstens einem Meßaufnehmer zur mittelbaren oder unmittelbaren Bremskraftmessung versehenen Scherkraftmeßbolzen beinhaltet. Der Meßaufnehmer wird durch zwei Dehnmeßstreifen gebildet, welche in einer Halbbrücke verschaltet sind, welche mit einer entfernt vom Scherkraftmeßbolzen angeordneten ergänzenden Halbbrücke, einem variablen Widerstand und einem Verstärker durch entsprechende Leitungen in Verbindung stehen. Wegen der Zuordnung der einzelnen Leitungen sind zum Anschließen der aus den Dehnmeßstreifen am Meßort bestehenden Halbbrücke an den Rest der Meßeinrichtung Fachkräfte notwendig. Außerdem erschwert die dezentrale Anordnung der Bauelemente eine einfache Montage bzw. einen schnellen Austausch der Meßeinrichtung in toto.The generic US-A-4 805 740 describes an electromechanical Brake application device with a brake actuator for applying and / or releasing the brake and with a power converter for the implementation of the brake actuator emitted energy in a brake application movement, the Power converter arranged in the power flow, with at least one sensor for indirect or direct braking force measurement Includes shear force measuring pin. The sensor is replaced by two strain gauges formed, which are connected in a half bridge, which with a removed from the shear force measuring bolt arranged additional half bridge, one variable resistance and an amplifier through appropriate lines stay in contact. Because of the assignment of the individual lines to Connect the half-bridge consisting of the strain gauges at the measuring location specialists to the rest of the measuring device. It also complicates decentralized arrangement of the components a simple assembly or a quick exchange of the measuring device in total.

Der vorliegenden Erfindung liegt demgegenüber die Aufgabe zugrunde, eine elektromechanische Bremszuspanneinrichtung der eingangs erwähnten Art zu schaffen, bei welcher die Montage, der Austausch oder die Umrüstung der Meßeinrichtung vereinfacht ist.The present invention is based on the object, a Electromechanical brake application device of the type mentioned at the beginning create, in which the assembly, exchange or retrofitting of Measuring device is simplified.

Erfindungsgemäß wird diese Aufgabe durch die kennzeichnenden Merkmale von Anspruch 1 gelöst. According to the invention, this object is achieved by the characterizing features solved by claim 1.

Vorteile der ErfindungAdvantages of the invention

Indem erfindungsgemäß die Auswerteelektronik im Bolzenkopf des Scherkraftmeßbolzens enthalten ist, bildet der Scherkraftmeßbolzen ein komplettes Meßmodul, welches der Bremskraftregelung Signale liefert, die proportional zur Ist-Bremskraft sind. Beispielsweise wird das von den Dehnmeßstreifen gelieferte Widerstandssignal ΔR durch die Auswerteelektronik in ein analoges Signal (-10 V bis +10V) oder ein digitales, zur Bremskraft proportionales Signal gewandelt. Damit kann der erfindungsgemäße Scherkraftmeßbolzen als in sich geschlossenes Meßmodul in den Regelkreis beliebiger Bremszuspanneinrichtungen integriert werden, was die Montage, den Austausch oder die Umrüstung stark vereinfacht. Insbesondere weist der Scherkraftmeßbolzen dann nur eine standardisierte Schnittstelle auf, welche auch von Nicht-Fackräften an eine Bremskraftregeleinrichtung angeschlossen werden kann.According to the invention, the evaluation electronics in the bolt head of the shear force measuring bolt is included, the shear force measuring bolt forms a complete measuring module, which provides the braking force control with signals that are proportional to the actual braking force are. For example, the resistance signal provided by the strain gauges ΔR by the evaluation electronics into an analog signal (-10 V up to + 10V) or a digital signal proportional to the braking force. In order to can the shear force measuring pin according to the invention as a self-contained Measuring module integrated in the control circuit of any brake application devices which greatly simplifies assembly, replacement or retrofitting. In particular, the shear force measuring pin then only has a standardized one Interface on, which also from non-torch forces to a braking force control device can be connected.

Der mechatronische Scherkraftmeßbolzen vereinigt mit Kraftumsetzung und gleichzeitiger Kraftmessung zwei Funktionen in sich. Daher kann die erfindungsgemäße Bremszuspanneinrichtung zum einen klein bauen, zum anderen ergeben sich weniger Bauelemente und ein geringeres Gewicht. Indem der Kraftsensor direkt und unmittelbar in den Kraftfluß des Kraftumsetzers integriert ist, ergibt sich darüber hinaus eine hohe Meßgenauigkeit. Der Scherkraftmeßbolzen kann mechanisch hoch dauerfest ausgelegt werden, zur Gewährleistung einer sicheren Kraftübertragung.The mechatronic shear force measuring pin combines with force conversion and simultaneous force measurement two functions in themselves. Therefore, the invention Build brake application device on the one hand, on the other hand there are fewer components and a lower weight. By the force sensor is integrated directly and immediately into the power flow of the power converter, results there is also high measuring accuracy. The shear force measuring pin can be designed mechanically highly durable to ensure a safe Power transmission.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Patentanspruch 1 angegebenen Bremszuspanneinrichtung möglich.The measures listed in the subclaims are advantageous Developments and improvements to that specified in claim 1 Brake application device possible.

Gemäß einer besonders zu bevorzugenden Ausführungsform der Erfindung bildet der Scherkraftmeßbolzen einen Gelenkbolzen eines wenigstens zwei Kraftübertragungselemente des Kraftumsetzers miteinander verbindenden Gelenks. Das Gelenk lenkt einen vom Bremsaktuator linear betätigbaren Pleuel an einen Bremshebel einer auf Bremsbacken wirkenden Exzenteranordnung an. Hierdurch befindet sich die Kraftmeßstelle in unmittelbarer Nähe der Kraftwirkstelle, weshalb der Einfluß von Störgrößen wie beispielsweise Lagerreibung oder Hysterese gering ist, so daß dadurch sehr genaue Messungen möglich werden.According to a particularly preferred embodiment of the invention the shear force measuring pin forms a hinge pin of at least two force transmission elements of the power converter connecting joint. The joint directs a connecting rod that can be actuated linearly by the brake actuator to one Brake lever of an eccentric arrangement acting on brake shoes. hereby the force measuring point is in the immediate vicinity of the force acting point, which is why the influence of Disturbances such as bearing friction or hysteresis is small, so that very precise measurements are possible.

Eine bevorzugte Maßnahme sieht vor, daß der Meßaufnehmer zur Bremskraftmessung wenigstens einen am Umfang des Scherkraftmeßbolzens gehaltenen Dehnmeßstreifen beinhaltet. Dehnmeßstreifen haben bekanntermaßen eine hohe Meßgenauigkeit bei gleichzeitig breitem Meßbereich und sind unempfindlich gegenüber Temperatur-änderungen und Druckstößen, was vor allem bei der im Rahmen von Notbremsungen schlagartig eintretenden Krafteinwirkung von Vorteil ist. Darüber zeichnen sie sich durch eine gute Langzeitstabilität sowie hohe Korrosionsbeständigkeit aus.A preferred measure provides that the sensor for braking force measurement at least one strain gauge held on the circumference of the shear force measuring bolt includes. Strain gauges are known to have high measuring accuracy with a wide measuring range at the same time and are insensitive to Temperature changes and pressure surges, which is especially true in the context of Emergency braking sudden force is advantageous. About that they are characterized by good long-term stability and high corrosion resistance out.

Gemäß einer Weiterbildung sind redundante Meßaufnehmer und/oder redundante Sensorsignal-Auswerteelektroniken, insbesondere redundante Meßaufnehmer mit unterschiedlichen Meßprinzipien und/oder redundante Sensorsignal-Auswerteelektroniken unterschiedlichen Aufbaus und Art vorgesehen. Damit wird eine erhöhte Zuverlässigkeit der Meßanordnung erzielt, außerdem ist eine Plausibilitätsprüfung durch Vergleich der Meßsignale zweier oder mehrerer Meßkreise möglich.According to a further development, redundant sensors and / or redundant ones Sensor signal evaluation electronics, in particular redundant sensors with different measuring principles and / or redundant sensor signal evaluation electronics different construction and type. So that will an increased reliability of the measuring arrangement is achieved, moreover a plausibility check is carried out possible by comparing the measurement signals of two or more measuring circuits.

Zeichnungendrawings

Ein Ausführungsbeispiel der Erfindung ist in den Zeichnungen dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen :

  • Fig.1 eine Schnittdarstellung einer bevorzugten Ausführungsform eines erfindungsgemäßen Bremsaktuators mit einem integrierten Scherkraftmeßbolzen;
  • Fig.2 eine Schnittdarstellung des Scherkraftmeßbolzens von Fig.1 entlang der Linie II-II.
    • An embodiment of the invention is shown in the drawings and explained in more detail in the following description. Show it :
  • 1 shows a sectional view of a preferred embodiment of a brake actuator according to the invention with an integrated shear force measuring bolt;
  • 2 shows a sectional view of the shear force measuring pin of FIG. 1 along the line II-II.

    • Beschreibung des AusführungsbeispielsDescription of the embodiment

    Die in Fig.1 insgesamt mit 1 bezeichnete, bevorzugte Ausführungsform einer elektromechanischen Bremszuspanneinrichtung ist für ein Schienenfahrzeug vorgesehen und beinhaltet einen Bremsaktuator 2 mit einer Betriebsbremseinheit und einer Speicherbremseinheit. Die Betriebsbremseinheit hat einen elektrischen Antrieb, beispielsweise einen elektrischen Stellmotor 4, der in einem Aktuatorgehäuse 6 des Bremsaktuators 2 untergebracht ist. Ein mechanischer Kraftumsetzer 8 dient zur Umsetzung der vom Bremsaktuator 2 abgegebenen Energie in eine Bremszuspannbewegung.The preferred embodiment of an electromechanical, designated overall by 1 in FIG Brake application device is provided for a rail vehicle and includes a brake actuator 2 with a service brake unit and one Brake unit. The service brake unit has an electric drive, for example an electric servomotor 4, which is in an actuator housing 6 of the Brake actuator 2 is housed. A mechanical force converter 8 is used for Conversion of the energy output by the brake actuator 2 into a brake application movement.

    Der Stellmotor 4 versetzt eine koaxiale Bremsspindel 10 in Drehung, welche durch den Kraftumsetzer 8 in eine Bremszuspannbewegung von Bremsbelägen 12 in Richtung auf eine Bremsscheibe 14 gewandelt werden. Der Kraftumsetzer 8 umfaßt unter anderem eine Spindel/Mutter-Baueinheit 16 mit einer auf der Bremsspindel 10 drehbar gelagerten Spindelmutter 18, welche bei Drehung der Bremsspindel 10 Linearbewegungen in Richtung der Spindelachse ausführen kann. Das vom Stellmotor 4 abgewandte Ende der Bremsspindel 10 ragt in einen zylindrischen Hohlabschnitt eines Pleuels 20 hinein, der mit der Spindelmutter 18 axialfest verbunden ist. Außerdem ist der zylindrische Hohlabschnitt des Pleuels 20 in einer Schiebehülse 22 axialfest gehalten, gegen welche wenigstens eine sich am Aktuatorgehäuse 6 abstützende Speicherfeder 24 in Bremslösestellung vorgespannt ist. Die Speicherfeder 24 ist Teil der Speicherbremseinheit und dient als Energiespeicher zum Speichern und Abgeben von Energie zum Zuspannen der Bremse als betriebliche Notbremse im Sinne einer unterlegten Sicherheitsebene bei Ausfall der Betriebsbremseinheit und/oder als Park- oder Feststellbremse. Sowohl die Betriebs- als auch die Speicherbremseinheit wirken auf den Pleuel 20. Die Speicherfeder 24 ist durch eine Verriegelungseinrichtung 26 in der vorgespannten Stellung gehalten.The actuator 4 sets a coaxial brake spindle 10 in rotation, which by the power converter 8 in a brake application movement of brake pads 12 in Direction to be converted to a brake disc 14. The power converter 8 includes including a spindle / nut assembly 16 with one on the brake spindle 10 rotatably mounted spindle nut 18, which 10 linear movements when the brake spindle rotates can run in the direction of the spindle axis. That from the servomotor 4 opposite end of the brake spindle 10 projects into a cylindrical hollow section a connecting rod 20, which is axially fixed to the spindle nut 18. Moreover the cylindrical hollow section of the connecting rod 20 is axially fixed in a sliding sleeve 22 held against which at least one is supported on the actuator housing 6 Storage spring 24 is biased in the brake release position. The storage spring 24 is part of the storage brake unit and serves as an energy storage for storage and Delivering energy to apply the brake as an operational emergency brake in the In the sense of an underlying security level in the event of failure of the service brake unit and / or as a parking or parking brake. Both the service and storage brake unit act on the connecting rod 20. The spring 24 is by a locking device 26 held in the biased position.

    Ein plattenförmiger Pleuelkopf 28 des Pleuels 20 ragt aus der Schiebehülse 22 heraus und ist mit einem Pleuelauge 30 versehen. Wie insbeondere aus Fig.2 hervorgeht, durchragt ein Gelenkbolzen 32 das Pleuelauge 30 sowie hierzu koaxiale Durchgangsbohrungen 34 von das Pleuelauge 30 axial umgreifenden, an einem Ende eines Bremshebels 36 ausgebildeten Wangen 38. Die Wangen 38 des Bremshebels 36, der Pleuelkopf 28 und der Gelenkbolzen 32 bilden zusammen ein Gelenk 40 des Kraftumsetzers 8, wodurch der Bremshebel 36 am Pleuel 20 senkrecht zur Spindelachse 42 angelenkt ist. Bei Antrieb der Bremsspindel 10 in Bremszuspannrichtung bzw. bei Lösen der Verriegelungseinrichtung 26 der Speicherfeder 24 wird aufgrund des dann axial ausfahrenden Pleuels 20 der Gelenkbolzen 32 unter anderem durch im wesentlichen senkrecht zur Bolzenachse 44 angreifende Scherkräfte beansprucht. A plate-shaped connecting rod head 28 of the connecting rod 20 protrudes from the sliding sleeve 22 and is provided with a connecting rod eye 30. As can be seen in particular from FIG. 2, a pivot pin 32 projects through the connecting rod eye 30 and coaxially with it Through bores 34 of the connecting rod eye 30 axially encompassing at one end a cheek 38 formed cheeks 38. The cheeks 38 of the brake lever 36, the connecting rod head 28 and the joint pin 32 together form a joint 40 of the power converter 8, whereby the brake lever 36 on the connecting rod 20 perpendicular to Spindle axis 42 is articulated. When driving the brake spindle 10 in the brake application direction or when the locking device 26 is released, the storage spring 24 becomes due to the connecting rod 20, which then extends axially, the joint pin 32 among other things by shear forces acting essentially perpendicular to the pin axis 44 claimed.

    Das andere Ende des Bremshebels 36 wirkt auf eine Exzenteranordnung mit einer Exzenterwelle 46, die an einen Zangenhebel 48 angelenkt ist, der zusammen mit einem weiteren Zangenhebel 50 eine Bremszange 52 bildet. An den einen Enden der Zangenhebel 48, 50 sind jeweils Belaghalter 54 mit Bremsbelägen 12 angeordnet, die in Richtung der Achse der Bremsscheibe 14 verschieblich sind. Die von den Bremsbelägen 12 abgewandt liegenden Enden der Zangenhebel 48, 50 sind miteinander über einen Druckstangensteller 56 verbunden, der vorzugsweise elektrisch betätigt ausgelegt ist. Die beschriebene Anordnung bildet ebenfalls einen Teil des Kraftumsetzers 8, der die vom Stellmotor 4 oder von der Speicherfeder 24 veranlaßten Ausfahrbewegungen des Pleuels 20 in eine Bremszuspannbewegung der Bremsbeläge 12 in Richtung auf die Bremsscheibe 14 wandelt.The other end of the brake lever 36 acts on an eccentric arrangement with a Eccentric shaft 46, which is articulated to a pliers lever 48, which together with another caliper lever 50 forms a brake caliper 52. At one end the caliper levers 48, 50 are each pad holders 54 with brake pads 12, which are displaceable in the direction of the axis of the brake disc 14. The one from the Brake pads 12 opposite ends of the caliper levers 48, 50 are together connected via a push rod actuator 56, which is preferably electrically is actuated. The arrangement described also forms part of the Power converter 8, which caused by the servomotor 4 or the storage spring 24 Extension movements of the connecting rod 20 in a brake application movement of the Brake pads 12 converts towards the brake disc 14.

    Erfindungsgemäß wird der Gelenkbolzen 32 des Gelenks 40 durch einen Scherkraftmeßbolzen 58 gebildet. Der Scherkraftmeßbolzen ist mit wenigstens einem Meßaufnehmer 60 zur Messung von Größen versehen, aus welchen die an den Bremsbelägen 12 wirkende Bremskraft mittelbar oder unmittelbar ableitbar ist. In bevorzugter Ausführungsform wird der Meßaufnehmer durch Dehnmeßstreifen (DMS) 60 gebildet, welche beispielsweise in einer Ebene senkrecht zur Bolzenachse 44 umlaufenden Nuten 62 aufgenommen sind. Die Nuten 62 mit den Dehnmeßstreifen 60 befinden sich im Bereich der axialen Stoßstellen des Pleuelkopfes 28 mit den Wangen 38 des Bremshebels 36 und somit genau in den Scherebenen des auf Scherung beanspruchten Scherkraftmeßbolzens 58. Die Dehnmeßstreifen 60 sind am Umfang des Scherkraftmeßbolzens 58 vorzugsweise durch Klebung derart befestigt, daß sie den aufgrund der gegensinnig wirkenden Scherkräfte hervorgerufenen Scherverformungen des Scherkraftmeßbolzens 58 proportionale Signale erzeugen und diese an eine Auswerteelektronik 64 liefern.According to the hinge pin 32 of the hinge 40 by a Shear force measuring pin 58 formed. The shear force measuring bolt is with at least one Provide sensor 60 for measuring quantities from which the to Brake pads 12 acting braking force can be derived indirectly or directly. In In a preferred embodiment, the sensor is made using strain gauges (DMS) 60 formed, for example, in a plane perpendicular to the bolt axis 44 circumferential grooves 62 are added. The grooves 62 with the strain gauges 60 are located in the area of the axial joints of the connecting rod head 28 with the cheeks 38 of the brake lever 36 and thus exactly in the shear plane of the shear force measuring pin 58 subjected to shear. The strain gauges 60 are preferably on the circumference of the shear force measuring bolt 58 by gluing attached that they are caused by the opposing shear forces Shear deformations of the shear force measuring pin 58 generate proportional signals and deliver them to evaluation electronics 64.

    Alternativ können die Nuten 62 entfallen und die Dehnmeßstreifen 60 auch direkt an der äußeren Mantelfläche des Scherkraftmeßbolzens 58 festgelegt sein. Gemäß einer weiteren Alternative oder zusätzlich können Dehnmeßstreifen 60 in einer zur Bolzenachse 44 koaxialen Hohlbohrung des Scherkraftmeßbolzens 58 gehalten sein, wobei dieser dann dünnwandig ausgeführt ist. Anstatt am Scherkraftmeßbolzen 58 oder zusätzlich hierzu können auch ein oder mehrere Dehnmeßstreifen 60 am Bremshebel 36 angeordnet sein, um aus den Verformungen des Bremshebels 36 die Bremskräfte ableiten zu können. Alternatively, the grooves 62 can be omitted and the strain gauges 60 can also be applied directly the outer surface of the shear force measuring pin 58 can be fixed. According to one another alternative or in addition, strain gauges 60 in one for Bolt axis 44 coaxial hollow bore of the shear force measuring pin 58 held be, which is then thin-walled. Instead of the shear force measuring pin 58 or in addition to this, one or more strain gauges 60 can also be Brake lever 36 may be arranged to the from the deformation of the brake lever 36 To be able to derive braking forces.

    Darüber hinaus kann jegliche andere Art von Meßaufnehmer verwendet werden, mit welchen die im Betrieb auftretenden Verformungen des Scherkraftmeßbolzens 58 und/oder des Bremshebels 36 meßbar sind, so beispielsweise in den Scherkraftmeßbolzen 58 integrierte Druckmessumformer, die vorzugsweise nach kapazitivem, piezoelektrischem oder piezoresistivem Prinzip arbeiten. Um eine möglichst hohe Zuverlässigkeit der Meßanordnung zu erzielen, können die Meßaufnehmer 60 und/oder die Auswertelektronik 64 redundant vorgesehen sein. Insbesondere können auch redundante Meßaufnehmer mit unterschiedlichen Meßprinzipien und redundante Auswerteelektroniken unterschiedlichen Aufbaus und Art vorhanden sein.In addition, any other type of sensor can be used with which the deformations of the shear force measuring bolt 58 occurring during operation and / or the brake lever 36 can be measured, for example in the shear force measuring bolt 58 integrated pressure transmitters, which are preferably based on capacitive, work piezoelectric or piezoresistive principle. To be as high as possible To achieve reliability of the measuring arrangement, the measuring sensors 60 and / or the evaluation electronics 64 can be provided redundantly. In particular can also redundant sensors with different measuring principles and redundant Evaluation electronics of various designs and types are available.

    Der Scherkraftmeßbolzen 58 hat einen endseitigen, im Durchmesser vergrößerten Bolzenkopf 66, in welchem eine Sensorsignal-Auswerteelektronik 64 untergebracht ist, vorzugsweise dadurch, daß sie in den Bolzenkopf 66 eingegossen ist, wodurch eine schwingsdämpfende oder schwingungsentkoppelte Aufnahme gegeben ist. Bei den vorzugsweise verwendeten Dehnmeßstreifen 60 beinhaltet die Auswertelektronik 64 eine DMS-Brückenschaltung. Im Montagezustand schlägt eine stirnseitig Ringfläche des Bolzenkopfes 66 axial auf der oberen Wange 38 des Bremshebels 36 an, das vom Bolzenkopf 66 weg weisende Ende des Scherkraftmeßbolzens 58 hat zwei quer zur Bolzenachse 44 verlaufende Außennuten 68 zur Aufnahme eines lagesichernden Sprengrings.The shear force measuring pin 58 has an end-side, enlarged in diameter Bolt head 66, in which a sensor signal evaluation electronics 64 are accommodated is, preferably in that it is cast into the bolt head 66, whereby a vibration-damping or vibration-decoupled recording is given. at the preferably used strain gauge 60 contains the evaluation electronics 64 a strain gauge bridge circuit. In the assembled state, one strikes at the front Annular surface of the bolt head 66 axially on the upper cheek 38 of the brake lever 36, the end of the shear force measuring pin 58 pointing away from the pin head 66 has two outer grooves 68 extending transversely to the pin axis 44 for receiving one position-securing snap ring.

    In der Auswertelektronik 64 findet außerdem eine Umrechnung der Scherverformungssignale in Signale für die jeweils an den Bremsbelägen 12 wirkende Ist-Bremskraft statt, welche an eine nicht dargestellte Steuerungs- und Regelungseinrichtung weitergeleitet werden, um anhand eines Soll-Ist-Vergleichs eine gewünschte Soll-Bremskraft einregeln zu können. Darüber hinaus dienen die empfangenen Signale für die Ist-Bremskräfte zur Überwachung der Krafteinsteuerung und Funktionsfähigkeit der Bremszuspanneinrichtung 1 bei sicherheitsrelevanten Bremsungen. Zur Verifizierung der Meßergebnisse kann außerdem der antriebsseitig durch einen Stromsensor gemessene Motorstrom mit dem Signal für die Ist-Bremskraft abgeglichen werden. A conversion of the shear deformation signals also takes place in the evaluation electronics 64 in signals for the actual braking force acting on the brake pads 12 instead, which to a control and regulation device, not shown forwarded to a desired based on a target-actual comparison To be able to adjust the target braking force. The received signals also serve for the actual braking forces for monitoring the force control and functionality the brake application device 1 for safety-relevant braking. to Verification of the measurement results can also be done by a Current sensor measured motor current compared with the signal for the actual braking force become.

    BezugszahlenlisteLIST OF REFERENCE NUMBERS

    11
    Bremszuspanneinrichtungbrake application
    22
    Bremsaktuatorbrake actuator
    44
    Stellmotorservomotor
    66
    Aktuatorgehäuseactuator housing
    88th
    Kraftumsetzerpower converter
    1010
    Bremsspindelbrake spindle
    1212
    Bremsbelagbrake lining
    1414
    Bremsscheibebrake disc
    1616
    Spindel-Mutter-BaueinheitScrew and nut assembly
    1818
    Spindelmutterspindle nut
    2020
    Pleuelpleuel
    2222
    Schiebehülsesliding sleeve
    2424
    Speicherfederstorage spring
    2626
    Verriegelungseinrichtunglocking device
    2828
    Pleuelkopfsmall end
    3030
    Pleuelaugeconnecting rod
    3232
    Gelenkbolzenhinge pins
    3434
    DurchgangsbohrungenThrough holes
    3636
    Bremshebellever
    3838
    WangenWangen
    4040
    Gelenkjoint
    4242
    Spindelachsespindle axis
    4444
    Bolzenachsepin axis
    4646
    Exzenterwelleeccentric shaft
    4848
    Zangenhebel caliper lever
    5050
    Zangenhebelcaliper lever
    5252
    Bremszangecaliper
    5454
    Belaghalterpad holders
    5656
    DruckstangenstellerPlunger rod adjuster
    5858
    Scherkraftmeßbolzenshearing force measuring
    6060
    Meßaufnehmer (DMS)Sensor (DMS)
    6262
    Nutengroove
    6464
    Auswerteelektronikevaluation
    6666
    Bolzenkopfbolt head
    6868
    Außennuten.Outer grooves.

    Claims (14)

    1. Electromechanical brake application device (1), in particular for a rail vehicle brake, comprising a brake actuator (2) for the application and/or release of the brake and a force converter (8) for converting the energy released by the brake actuator (2) into a brake application movement, wherein the force converter (8) contains a shear force measuring screw (58) arranged in the force flow and provided with at least one measuring sensor for indirect or direct braking force measurement, characterised in that measuring sensor signal evaluation electronics (64) are arranged in an end screw head (66), which is enlarged in diameter, of the shear force measuring screw (58).
    2. Electromechanical brake application device according to claim 1, characterised in that the shear force measuring screw (58) forms a hinge pin (32) of a joint (40) connecting at least two force transmission elements (20, 36) of the force converter (8) to one another.
    3. Electromechanical brake application device according to claim 2, characterised in that the joint (40) connects a connecting rod (20), which can be linearly actuated by the brake actuator, to a brake lever (36) of an eccentric arrangement acting on brake linings (12).
    4. Electromechanical brake application device according to claim 3, characterised in that the shear force measuring screw (58) penetrates a connecting rod head (28) of the connecting rod (20) as well as through-holes (34), which are coaxial to this, of cheeks (38) of the brake lever (36) axially encompassing the connecting rod head (28).
    5. Electromechanical brake application device according to claim 4, characterised in that the brake lever (36) acts on an eccentric arrangement with an eccentric shaft (46) which is articulated to at least one forked lever (48), which together with a further forked lever (50) forms a brake calliper (52), lining holders with brake linings (12), which are displaceable in the direction of an axis of a brake disc (14), being arranged at the ends of the forked levers (48, 50).
    6. Electromechanical brake application device according to any one of the preceding claims, characterised in that the measuring sensor contains at least one strain guage (60) held at the periphery of the shear force measuring screw (58) for indirect or direct braking force measurement.
    7. Electromechanical brake application device according to any one of the preceding claims, characterised in that the measuring sensor contains at least one strain guage (60) held in a hollow hole of a thin-walled shear force measuring screw for indirect or direct braking force measurement.
    8. Electromechanical brake application device according to any one of the preceding claims, characterised in that provided at the periphery of the shear force measuring screw (58) are recesses (62) for receiving the strain guages (60), which are located in the region of axial impact planes of the connecting rod head (28) with the cheeks (38) of the brake lever (36),
    9. Electromechanical brake application device according to any one of the preceding claims, characterised in that the measuring sensor (60) contains at least one pressure measurement converter integrated in the shear force measuring screw (58), preferably a pressure measurement converter operating according to a capacitive, piezoelectric or piezoresistive principle, for indirect or direct braking force measurement.
    10. Electromechanical brake application device according to any one of the preceding claims, characterised in that the measuring sensor signal evaluation electronics (64) are sealed in a shakeproof and shockproof manner in the screw head (66).
    11. Electromechanical brake application device according to claim 10, characterised in that redundant measuring sensors (60) and/or redundant measuring sensor signal evaluation electronics (64), in particular redundant measuring sensors with different measuring principles and/or redundant measuring sensor signal evaluation electronics of different construction and type are provided.
    12. Electromechanical brake application device according to claim 11, characterised in that actual values for the instantaneous braking force can be supplied as signals to a regulation device by the measuring sensor (60).
    13. Electromechanical brake application device according to any one of the preceding claims, characterised in that the brake actuator (2) contains an electric motor (4), the motor current of which can be detected by a current sensor.
    14. Electromechanical brake application device according to claim 13, characterised in that the signal for the motor current can be balanced with the signal for the braking force.
    EP02710051A 2001-02-12 2002-01-30 Electro mechanical brake tightening device Expired - Lifetime EP1362194B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    DE10106378 2001-02-12
    DE10106378A DE10106378C2 (en) 2001-02-12 2001-02-12 Electromechanical brake application device
    PCT/EP2002/000930 WO2002064990A1 (en) 2001-02-12 2002-01-30 Electro mechanical brake tightening device

    Publications (2)

    Publication Number Publication Date
    EP1362194A1 EP1362194A1 (en) 2003-11-19
    EP1362194B1 true EP1362194B1 (en) 2004-10-20

    Family

    ID=7673707

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP02710051A Expired - Lifetime EP1362194B1 (en) 2001-02-12 2002-01-30 Electro mechanical brake tightening device

    Country Status (6)

    Country Link
    US (1) US6957571B2 (en)
    EP (1) EP1362194B1 (en)
    JP (1) JP4285995B2 (en)
    AT (1) ATE280339T1 (en)
    DE (2) DE10106378C2 (en)
    WO (1) WO2002064990A1 (en)

    Families Citing this family (13)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    DE10148472A1 (en) * 2001-10-01 2003-04-17 Knorr Bremse Systeme Disc brake and method for determining the braking force of a disc brake
    DE10214669B4 (en) * 2002-04-03 2014-01-23 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Method and device for controlling an electrically operated wear adjustment device
    DE10245207C1 (en) * 2002-09-27 2003-10-23 Knorr Bremse Systeme Brake operating device for rail vehicle brake, has shear force measuring bolt used for incorporated brake force measurement
    EP1839983B1 (en) 2006-03-29 2016-03-16 Meggitt SA Apparatus for measuring the braking force in an aircraft brake assembly
    DE102006029978B3 (en) * 2006-06-29 2007-11-08 Siemens Ag Disc brake`s e.g. floating caliper-disc brake, operative axial force measuring method for use in motor vehicle, involves receiving shearing movement of part of disc brake by sensor to balance back to actual operative axial force
    US8800697B2 (en) * 2009-09-01 2014-08-12 Ryno Motors, Inc. Electric-powered self-balancing unicycle with steering linkage between handlebars and wheel forks
    DE102009051352A1 (en) * 2009-10-30 2011-05-05 Siemens Aktiengesellschaft Disc brake device for rail vehicles
    RU2564460C2 (en) * 2010-02-02 2015-10-10 Кнорр-Бремзе Зюстеме Фюр Шиненфарцойге Гмбх Actuator with pressure bar for compact modules with disc brake support with threaded part resting directly on actuator body
    US9616875B2 (en) 2014-09-11 2017-04-11 Westinghouse Air Brake Technologies Corporation Piston stroke sensor arrangement for a brake unit
    US10119873B2 (en) 2014-09-15 2018-11-06 Westinghouse Air Brake Technologies Corporation Brake force sensor arrangement for a brake unit
    ES2733451T3 (en) * 2016-08-25 2019-11-29 Dellner Brakes Ab A lever type braking device
    IT202000007003A1 (en) * 2020-04-02 2021-10-02 Faiveley Transport Italia Spa Electromechanical service and emergency braking actuator for a railway vehicle and electromechanical braking system
    JP6792094B1 (en) * 2020-07-31 2020-11-25 三菱重工エンジニアリング株式会社 Brake caliper device

    Family Cites Families (22)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    DE3344616A1 (en) * 1983-12-09 1985-06-20 Knorr-Bremse GmbH, 8000 München BRAKE UNIT FOR RAIL VEHICLES
    JPS61145426A (en) * 1984-12-19 1986-07-03 Hitachi Constr Mach Co Ltd Load measuring apparatus
    DE3543456C2 (en) * 1985-12-09 1993-11-11 Knorr Bremse Ag Brake caliper for disc brakes
    EP0267973B1 (en) * 1986-11-11 1992-02-12 Black & Decker Inc. Power driven saw, in particular electrically powered saw
    DE3709952C1 (en) * 1987-03-26 1988-08-25 Richard Dipl-Ing Wilke Electromotive brake actuation device for rail vehicles
    DE4024811C2 (en) * 1990-08-04 1997-02-20 Telefunken Microelectron Device for controlling the braking process of motor vehicles
    DE19548392C2 (en) * 1995-12-22 2001-05-17 Siemens Ag Brake system for a motor vehicle
    DE19607759C1 (en) * 1996-03-01 1997-05-28 Korthaus Bernd Dipl Kaufm Electric brake operating device for rail vehicle brake mechanism
    DE19652230A1 (en) * 1996-12-16 1998-06-18 Teves Gmbh Alfred Electromechanically actuated disc brake
    DE19653427A1 (en) * 1996-12-20 1998-07-02 Siemens Ag Force sensor
    EP1032518B1 (en) * 1997-11-22 2003-05-28 Continental Teves AG & Co. oHG Electromechanical brake system
    DE19828700A1 (en) * 1998-04-30 1999-11-11 Thomas Loeffler Bolt with information storage device for high quality joints enables simple documentation of e.g. tightening force
    EP1016614B1 (en) 1998-07-16 2004-09-22 Mitsubishi Denki Kabushiki Kaisha Controller for elevators
    JP2001019292A (en) * 1999-06-25 2001-01-23 Inventio Ag Device and method to prevent vertical directional displacement and vertical directional vibration of load support means of vertical carrier device
    JP3736225B2 (en) * 1999-09-14 2006-01-18 日産自動車株式会社 Electric brake device
    DE19945701A1 (en) * 1999-09-23 2001-04-19 Knorr Bremse Systeme Brake actuator
    DE29923681U1 (en) * 1999-09-23 2001-01-18 Knorr Bremse Systeme Application device for a vehicle brake
    DE10027667B4 (en) * 2000-06-03 2010-04-08 Robert Bosch Gmbh Method and device for determining an underlying value of at least one measured variable of a brake system
    DE10058925B4 (en) * 2000-11-28 2006-06-01 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH brake actuator
    DE10061950C2 (en) * 2000-12-13 2002-11-21 Knorr Bremse Systeme Electromechanical brake actuator
    WO2002049897A1 (en) * 2000-12-19 2002-06-27 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Electromechanical brake applying device
    AU2002228006A1 (en) * 2000-12-19 2002-07-01 Knorr-Bremse Systeme Fur Schienenfahrzeuge Gmbh Brake actuator comprising an energy accumulator and an inertia weight

    Also Published As

    Publication number Publication date
    DE50201358D1 (en) 2004-11-25
    ATE280339T1 (en) 2004-11-15
    EP1362194A1 (en) 2003-11-19
    DE10106378A1 (en) 2002-09-12
    US20040069055A1 (en) 2004-04-15
    DE10106378C2 (en) 2003-03-06
    WO2002064990A1 (en) 2002-08-22
    US6957571B2 (en) 2005-10-25
    JP2004518100A (en) 2004-06-17
    JP4285995B2 (en) 2009-06-24

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